CN107531126B - Vehicle air conditioner - Google Patents

Abstract

The invention aims to provide an air conditioner for a vehicle, which can suppress noise and flow path resistance in spite of compact structure. An air conditioning device for a vehicle includes a centrifugal fan (200) and a casing (400). The centrifugal fan sucks air in a direction along a rotation axis (RC) from a fan suction port (210) by rotating around the rotation axis and blows out the air in a radial direction. The casing has a fan housing chamber (440), an introduction flow path (420), and a wall body (421). The fan chamber accommodates the centrifugal fan. The introduction flow path guides air taken in from the outside to the centrifugal fan by flowing the air in a first direction intersecting the rotation axis. The wall body separates the fan housing chamber from the introduction flow path, and an opening (422) is formed at a position facing the fan suction port. An annular protrusion (431) protruding from the wall toward the inflow path side and covering the opening is provided on the periphery of the opening.

Description

Vehicle air conditioner

Cross-reference of related applications

This application is based on the JP Patent application 2015-091133 for which it applied on April 28, 2015, The content of an indication is incorporated in this application as a reference.

technical field

The invention relates to a vehicle air conditioner.

Background technique

A known vehicle air conditioner includes: a centrifugal fan that sucks air in a direction along a rotation axis; and a case that accommodates the centrifugal fan. A flow path is formed inside the casing, and when the centrifugal fan rotates, air is drawn into the flow path from the interior and exterior of the vehicle by the negative pressure associated with the rotation.

The flow path inside the casing is equipped with temperature adjustment equipment such as an evaporator and a heater core. The air taken in the flow path is blown out into the vehicle interior after being appropriately temperature-regulated by these temperature adjustment devices. Regarding such a vehicle air conditioner, studies are being conducted for the purpose of reducing noise, flow path resistance, and the like that are generated due to suction of air.

On the other hand, Patent Document 1 below describes an air conditioner in which a guide member is provided at a location corresponding to a suction port of a centrifugal fan. The guide member has a conical shape protruding toward the suction port of the centrifugal fan. Since the air taken into the flow path inside the casing is smoothly directed to the suction port of the centrifugal fan by adjusting the air flow by the guide member, noise and flow path resistance can be suppressed.

In addition, the air conditioner described in the following Patent Document 1 is configured to take in air from opposite sides of a cube-shaped casing. By supplying air to the suction port of the centrifugal fan from two directions, the flow velocity distribution of the air at the suction port becomes substantially uniform.

prior art literature

patent documents

Patent Document 1: Japanese Patent Laid-Open No. 2008-241143

In recent years, there has been a growing demand for downsizing of equipment mounted on vehicles, and vehicle air conditioners are no exception. Therefore, it is often difficult to configure the flow path to supply air to the suction port of the centrifugal fan from other directions.

According to the study of the inventors of the present invention, even when air is supplied to the centrifugal fan from one direction, as long as the direction is along the rotation axis of the centrifugal fan, there is no major problem. However, when this direction is a direction intersecting with the rotation axis of the centrifugal fan, the flow velocity of the air may become locally larger at the suction port of the centrifugal fan. As a result, there are disadvantages such as noise at the suction port and increased flow path resistance.

Contents of the invention

The present invention has been made in view of the above points, and an object of the present invention is to provide a vehicle air conditioner capable of suppressing noise and flow path resistance despite having a compact structure.

A vehicle air conditioner according to the present invention includes a centrifugal fan and a casing. The centrifugal fan rotates around the rotation axis, and the fan inlet sucks air in a direction along the rotation axis, and blows the air radially. The casing has a fan housing chamber, an introduction flow path, and a wall. The fan housing accommodates the centrifugal fan. The introduction flow path causes air taken in from the outside to flow in a first direction intersecting the rotation axis and guides the air toward the centrifugal fan. The wall body separates the fan housing chamber from the introduction flow path, and an opening is formed at a portion facing the fan suction port. A ring-shaped protrusion protruding from the wall toward the introduction flow path and covering the opening is provided on a peripheral edge of the opening. The air conditioner for a vehicle is provided with a flange-shaped protrusion which is arranged at a distance from the wall and protrudes outward from the opening from the ring-shaped protrusion.

In the present invention, air taken in from the outside flows in a first direction crossing the rotation axis and is guided toward the centrifugal fan. In this case, there is a possibility that a distribution in which the flow velocity of the air locally increases in the upstream portion of the opening in the first direction.

Therefore, in the present invention, the annular protrusion protruding from the wall body toward the introduction flow path and covering the opening is provided on the periphery of the opening. Thereby, the air flow of the air introduced into the flow path can be dispersed around the opening by causing the air flow to flow along the annular protrusion, and the air can also be returned to the downstream side of the opening in the first direction. parts. As a result, it is possible to suppress the occurrence of a distribution in which the flow velocity of the air locally increases at the opening and the fan suction port, and it is possible to suppress noise and flow path resistance.

According to the present invention, it is possible to provide a vehicle air conditioner capable of suppressing noise and flow path resistance despite having a compact structure.

Description of drawings

The above-mentioned object and other objects, features, and advantages related to the present invention will be clarified by the following detailed description with reference to the accompanying drawings.

FIG. 1 is a cross-sectional view showing a vehicle air conditioner according to an embodiment of the present invention.

Fig. 2 is an enlarged view around the first centrifugal fan in Fig. 1 .

FIG. 3 is a cross-sectional view taken along line III-III in FIG. 1 .

4 is a cross-sectional view showing a vehicle air conditioner according to a modified example of the embodiment.

Detailed ways

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In order to make the description easier to understand, in each of the drawings, the same reference numerals are assigned to the same constituent elements as much as possible, and overlapping descriptions are omitted.

First, an outline of a vehicle air conditioner 100 according to an embodiment of the present invention will be described with reference to FIG. 1 .

Vehicle air conditioner 100 (hereinafter simply referred to as "air conditioner 100") is a device mounted on a vehicle for the purpose of adjusting the temperature in a vehicle interior (not shown). As shown in FIG. 1 , the air conditioner 100 includes a casing 400 , a first centrifugal fan 200 , a second centrifugal fan 300 , an evaporator 601 , and a heater core 602 .

The casing 400 is a member serving as a housing of the air conditioner 100 and is formed of a resin material. The casing 400 has a first introduction flow path 420 and a second introduction flow path 450 formed vertically partitioned by the partition wall 411 therein.

In addition, the casing 400 has an external air intake port 401 formed on the upper surface near one end thereof, and an internal air intake port 402 formed on the side surface near the one end portion. The outside air inlet 401 takes in the air outside the vehicle (outside air) into the casing 400 . The interior air inlet 402 takes in the air (interior air) in the vehicle interior into the casing 400 .

In addition, the housing 400 has a first fan housing chamber 440 and a second fan housing chamber 470 . The first fan housing chamber 440 is separated from the first introduction flow path 420 by the first wall body 421 , and is formed in a lower space near the other end of the housing 400 . A circular first opening 422 that communicates with the first introduction flow path 420 and the first fan housing chamber 440 is formed in the first wall body 421 . In addition, the second fan housing chamber 470 is separated from the second introduction flow path 450 by the second wall body 451 , and is a space formed in an upper portion close to the other end portion of the casing 400 . A circular second opening 452 that communicates with the second introduction flow path 450 and the second fan housing chamber 470 is formed in the second wall body 451 .

In addition, the casing 400 has a first outlet 403 formed on the lower surface near the other end, and a second outlet 404 is formed on the lower side surface near the other end. Both the first air outlet 403 and the second air outlet 404 communicate with the first fan housing chamber 440 and the outside of the casing 400 . In addition, the casing 400 has a third outlet 405 formed on the upper surface near the other end, and a fourth outlet 406 is formed on the upper side near the other end. Both the third outlet 405 and the fourth outlet 406 communicate with the second fan housing chamber 470 and the outside of the casing 400 .

The first centrifugal fan 200 is housed in the first fan housing chamber 440 of the housing 400 such that the fan suction port 210 faces the first opening 422 of the first wall 421 . The first centrifugal fan 200 has a plurality of blades 220 that are curved and arranged at equal intervals. A fan outlet 230 is formed on the radially outer side of the centrifugal fan 200 . The rotation axis RC which becomes the rotation center of the 1st centrifugal fan 200 is being fixed to the output shaft MT1 of the electric motor MT (refer FIG. 2).

The second centrifugal fan 300 is accommodated in the second fan accommodation chamber 470 of the casing 400 . The second centrifugal fan 300 has substantially the same shape as the aforementioned first centrifugal fan 200 , and has a fan inlet 310 facing the second opening 452 of the second wall 451 and a radially outer fan outlet 330 . The aforementioned rotating shaft RC is inserted through the first opening 422 and the second opening 452 and passes through the partition wall 411 , and the second centrifugal fan 300 is fixed to the rotating shaft RC.

The evaporator 601 is arranged so as to straddle the upstream side of the first introduction flow path 420 and the second introduction flow path 450 inside the casing 400 . The evaporator 601 is configured such that air can pass through the inside of the evaporator 601 by allowing air to flow in from one side of the evaporator 601 and flow out from the other side opposite to the one side. The evaporator 601 is a cooling heat exchanger that cools and dehumidifies the air passing through the interior by absorbing heat from the air and evaporating the low-pressure refrigerant in a refrigeration cycle (not shown), as is well known.

The heater core 602 is arranged so as to pass through the partition wall 411 and straddle the first introduction flow path 420 and the second introduction flow path 450 . The heater core 602 is configured such that air can pass through by allowing air to flow in from one side of the heater core 602 and allowing air to flow out from the other side opposite to the one side. Cooling water having a high temperature due to cooling an engine (not shown) mounted on the vehicle flows through the heater core 602 . The heater core 602 is a heating heat exchanger that heats the air passing through the interior by using the cooling water as a heat source.

Inside the housing 400 are provided an internal and external air door 512 , a first door 522 , and a second door 532 .

The inside and outside air door 512 is provided on the upstream side of the evaporator 601 . The inner-outer air door 512 is configured such that one end of the inner-outer air door 512 is connected to a hinge 511 , and is rotatable around the hinge 511 between a first position 512A and a second position 512B indicated by dotted lines. When the inside-outside air door 512 is arranged at the first position 512A, the outside-air inlet 401 is closed and the inside-air inlet 402 is opened. When the inside-outside air door 512 is arranged at the second position 512B, the outside-air inlet 401 is opened and the inside-air inlet 402 is closed. In addition, when the inside-outside air door 512 is arranged at the third position 512C between the first position 512A and the second position 512B, the outside-air inlet 401 and the inside-air inlet 402 are opened.

The first door 522 is provided in the first introduction flow path 420 on the downstream side of the heater core 602 . The first door 522 is configured such that one end of the first door 522 is connected to a hinge 521 and is rotatable around the hinge 521 between a first position 522A and a second position 522B indicated by a dotted line. When the first door 522 is arranged at the first position 522A, the downstream side of the part of the heater core 602 arranged in the first introduction flow path 420 is closed. On the other hand, when the first door 522 is arranged at the second position 522B, the downstream side of this part is opened.

The second door 532 is provided in the second introduction flow path 450 on the upstream side of the heater core 602 . The second door 532 is configured such that one end of the second door 532 is connected to a hinge 531 and is rotatable around the hinge 531 between a first position 532A and a second position 532B indicated by a dotted line. When the second door 532 is arranged at the first position 532A, the upstream side of the part of the heater core 602 arranged in the second introduction flow path 450 is closed. On the other hand, when the second door 532 is arranged at the second position 532B, the upstream side of this part is opened.

In the air conditioner 100 configured as described above, when electric power is supplied to the motor MT, the first centrifugal fan 200 and the second centrifugal fan 300 rotate around the rotation axis RC. The rotating first centrifugal fan 200 and second centrifugal fan 300 suck air through the first opening 422 and the second opening 452 , respectively, so that the first introduction flow path 420 and the second introduction flow path 450 become negative pressure.

When the first introduction flow path 420 and the second introduction flow path 450 become negative pressure, air is taken into the casing from at least one of the outside air inlet 401 and the inside air inlet 402 according to the arrangement of the inside and outside air doors 512 400's interior. The air is cooled and dehumidified by the evaporator 601 , and then flows into the first introduction channel 420 and the second introduction channel 450 .

The air flowing into the first introduction flow path 420 and the second introduction flow path 450 bypasses the heater core 602 or passes through the inside of the heater core 602 according to the arrangement of the first door 522 and the second door 532 .

That is, when the first door 522 is arranged at the first position 522A, the air in the first introduction flow path 420 flows downstream by bypassing the heater core 602 because the downstream side of the heater core 602 is closed. On the other hand, when the first door 522 is arranged at the second position 522B, the air in the first introduction flow path 420 flows downstream through the inside of the heater core 602 because the downstream side of the heater core 602 is opened.

Also, when the second door 532 is arranged at the first position 532A, the air in the second introduction flow path 450 flows downstream by bypassing the heater core 602 because the upstream side of the heater core 602 is closed. On the other hand, when the second door 532 is arranged at the second position 532B, the air in the second introduction flow path 450 flows downstream through the inside of the heater core 602 because the upstream side of the heater core 602 is opened.

When the heater core 602 is bypassed, the air flows downstream in a low-temperature state. On the other hand, when passing through the inside of the heater core 602, the temperature of the air is raised by heat exchange with high-temperature cooling water, and then flows downstream.

The air on the downstream side of the heater core 602 flows in the direction of arrow S1 along the first wall body 421 and the second wall body 451 in the first introduction flow path 420 and the second introduction flow path 450 , respectively. The direction of the arrow S1 is a first direction intersecting the rotation axis RC of the centrifugal fan 200 .

The air flowing in the direction of arrow S1 in the first introduction channel 420 reaches the first opening 422 of the first wall 421 after the directivity is adjusted by the annular protrusion 431 and the flange-shaped protrusion 432 . In addition, the air drawn by the fan inlet 210 of the first centrifugal fan 200 through the first opening 422 is blown out from the fan outlet 230 into the first fan housing chamber 440 . The air is blown out of the housing 400 from the first outlet 403 and the second outlet 404 .

In addition, the air flowing in the direction of arrow S1 in the second introduction channel 450 reaches the second opening 452 of the second wall 451 after the directivity is adjusted by the annular protrusion 461 and the flange-shaped protrusion 462 . In addition, the air sucked by the fan inlet 310 of the second centrifugal fan 300 through the second opening 452 is blown out from the fan outlet 330 into the second fan housing chamber 470 . The air is blown out of the housing 400 from the third outlet 405 and the fourth outlet 406 .

The air blown out from the first outlet 403 to the fourth outlet 406 is supplied to the inner surface of the windshield of the vehicle and the head of the occupant through a duct (not shown) in which a flow path is formed. , chest, feet and other parts of the car interior.

Next, the configuration around the first opening 422 will be described with reference to FIGS. 2 and 3 . In addition, since the structure around the second opening 452 is approximately vertically symmetrical with the structure around the first opening 422 , description thereof will be omitted here.

As shown in FIG. 2 , an annular protrusion 431 protruding toward the first introduction channel 420 and covering the first opening 422 is provided on the periphery of the first opening 422 of the first wall 421 . In this embodiment, the annular protrusion 431 is integrally formed with the first wall body 421 , but the present invention is not limited thereto. For example, the annular protrusion 431 may be formed as a member different from the first wall body 421 , and the annular protrusion 431 as a separate member may be provided on the first wall body 421 by means of bonding or the like.

The annular protrusion 431 is formed such that the protrusion amount Hu of a portion 431u upstream of the first introduction flow path 420 is greater than the protrusion amount Hd of a portion 431d downstream of the first introduction flow path 420 . In addition, the annular protrusion 431 has a gradual change portion 433 at the end portion on the first introduction channel 420 side. The gradient portion 433 has a curved shape with different radii of curvature. Specifically, the annular protrusion 431 is formed such that the radius of curvature Ru of the portion 433 u on the upstream side of the first introduction flow path 420 in the gradual change portion 433 is smaller than that of the portion 433 d on the downstream side of the first introduction flow path 420 in the gradual change portion 433 . The radius of curvature Rd is large.

In addition, a flange-shaped protrusion 432 is provided at the end of the protruding annular protrusion 431 . The flange-shaped protrusion 432 is arranged at a distance from the first wall body 421 . In addition, as shown in FIG. 3 , the flange-shaped protrusion 432 protrudes outward from the first opening 422 from the annular protrusion 431 , and has a substantially elliptical shape in plan view. Specifically, in the present embodiment, the protrusion amount of the flange-shaped protrusion 432 from the first opening 422 is larger at the upstream side of the flange-shaped protrusion 432 than at the downstream side of the flange-shaped protrusion 432 . . The annular protrusion 431 is arranged such that a gap is provided between the annular protrusion 431 and the inner wall surface 415 which is the downstream end of the first introduction channel 420 in the direction indicated by the arrow S1. In addition, the annular protrusion 431 is arranged such that a gap is provided between the annular protrusion 431 and the inner wall surfaces 413 , 414 of the first introduction channel 420 in the direction indicated by the arrow S2 . The direction indicated by the arrow S2 is a direction perpendicular to the rotation axis RC and the direction indicated by the arrow S1.

According to the structure around the first opening 422 as described above, as shown in FIG. , and reach the transition portion 433 as indicated by arrow S3. In addition, part of the air reaching the transition portion 433 is introduced into the first opening 422 along the curvature of the portion 433u, while the other portion of the air is within the range from the portion 433u to the portion 433d as indicated by arrow S5. It is introduced into the first opening 422 while turning on the transition portion 433 .

In addition, the air entering between the flange-shaped protrusion 432 and the first wall 421 among the air flowing in the direction indicated by the arrow S1 in the first introduction channel 420 follows the ring-shaped protrusion 431 as indicated by the arrow S4. The outer peripheral surface flows back to the downstream side. In addition, a part of the air that has entered between the flange-shaped protrusion 432 and the first wall body 421 flows along the surface of the annular protrusion 431 and rises as shown by the arrow S6 so as to pass over the annular protrusion 431 . However, since the flow of the air is restricted by the flange-shaped protrusion 432 , the air also flows along the outer peripheral surface of the annular protrusion 431 to flow back to the downstream side as indicated by arrow S4 .

As described above, in the present embodiment, the annular protrusion 431 protruding from the first wall body 421 toward the first introduction channel 420 to cover the first opening 422 is provided on the peripheral edge of the first opening 422 . Thus, by making the air in the first introduction flow path 420 flow along the annular protrusion 431 to disperse the air in the first introduction flow path 420 around the first opening 422 , the air can also flow back into the first opening. The portion on the downstream side in the direction indicated by the arrow S1 in the portion 422 . As a result, it is possible to suppress a distribution in which the flow velocity of the air locally increases in the first opening 422 and the fan suction port 210 , and it is possible to suppress noise and flow path resistance.

In addition, in this embodiment, a flange-shaped protrusion 432 is provided at a distance from the first wall body 421 and protrudes outward from the annular protrusion 431 to the outside of the first opening 422 . Thereby, the air flowing along the annular protrusion 431 can be suppressed from flowing into the first opening 422 beyond the annular protrusion 431 . As a result, the air can be further recirculated to the downstream portion of the first opening 422 in the direction indicated by the arrow S1, the occurrence of a distribution in which the flow velocity of the air is locally increased can be suppressed, and noise and flow passage can be reliably suppressed. resistance.

In addition, in the present embodiment, a gradation portion 433 is provided at the end portion of the annular protrusion 431 on the first introduction flow path 420 side. Thereby, the air reaching the gradual change portion 433 can be swirled around the rotation axis RC, and the air can be further returned to the downstream portion in the direction indicated by the arrow S1 in the first opening portion 422 . As a result, it is possible to suppress generation of a distribution in which the flow velocity of air locally increases, and it is possible to reliably suppress noise and flow path resistance.

In addition, in the present embodiment, the radius of curvature Ru of the portion 431 u on the upstream side of the first introduction flow path 420 in the gradual change portion 433 is larger than the radius of curvature Ru of the portion 431 d on the downstream side of the first introduction flow path 420 in the gradual change portion 433 . Big Rd. At the upstream portion 431 u where the air flow velocity is high, the radius of curvature Ru is increased to suppress separation of the air flow at the portion 431 u and to introduce air into the first opening 422 while suppressing turbulence of the air flow. On the other hand, in the portion 431d on the downstream side where the flow velocity of the air is low, even if the radius of curvature Rd is made small, detachment does not occur. In addition, by making the radius of curvature Rd small, protrusion of the downstream portion 432d of the flange-shaped protrusion 432 can be suppressed. That is, according to the present embodiment, although the flange-shaped protrusion 432 is configured in a compact shape, the turbulence of the air introduced into the first opening 422 can be suppressed. As a result, it is possible to suppress generation of a distribution in which the flow velocity of air locally increases, and it is possible to reliably suppress noise and flow path resistance.

In addition, in the present embodiment, the protrusion amount Hu of the portion 431 u of the annular protrusion 431 on the upstream side of the first introduction flow path 420 is larger than that of the portion 431 d of the annular protrusion 431 on the downstream side of the first introduction flow path 420 . The protrusion amount Hd is large. Accordingly, on the upstream side of the first introduction flow path 420 where the flow velocity of the air is high, the direct flow of air into the first opening 422 can be reliably suppressed by the portion 431 u protruding greatly. On the other hand, on the downstream side of the first introduction channel 420 where the flow velocity of air is low, the protrusion amount Hd of the portion 431d is small, so that the air returning to the downstream side can actively flow into the first opening 422 . As a result, it is possible to suppress generation of a distribution in which the flow velocity of air locally increases, and it is possible to reliably suppress noise and flow path resistance.

Next, a modified example of the embodiment of the present invention will be described with reference to FIG. 4 . In this modified example, the flange-shaped protrusion 432 of the above-mentioned embodiment is deformed into the flange-shaped protrusion 432A, and the configuration of other parts is the same as that of the above-mentioned embodiment. Therefore, the same reference numerals are assigned to the same configurations as those in the above-mentioned embodiment, and description thereof will be appropriately omitted.

Similar to FIG. 3 , FIG. 4 is a cross-sectional view of the air conditioner 100 along line III-III in FIG. 1 , and is a plan view of the flange-shaped protrusion 432A. As shown in FIG. 4 , the flange-shaped protrusion 432A is formed in a rectangular shape in plan view.

The flange-shaped protrusion 432A is formed over the range from the inner wall surface 413 at one end of the first introduction channel 420 to the inner wall surface 414 at the other end in the direction indicated by arrow S2 (second direction). That is, the end portion of the flange-shaped protrusion 432A is formed so as to be in contact with the inner wall surfaces 413 , 414 . The second direction refers to a direction perpendicular to the first direction indicated by the rotation axis RC and the arrow S1. On the other hand, the flange-shaped protrusion 432A is arranged such that a gap is provided between the flange-shaped protrusion 432A and the inner wall surface 415 which is the downstream end of the first introduction channel 420 in the direction indicated by the arrow S1.

In this modified example, similarly to the above-described embodiment, the protrusion amount of the flange-shaped protrusion 432A from the first opening 422 is larger than that of the flange-shaped protrusion 432A at the upstream side of the flange-shaped protrusion 432A. The part on the downstream side is large.

By forming the flange-shaped protrusion 432A in contact with the inner wall surfaces 413, 414 and not providing a gap between the flange-shaped protrusion 432A and the inner wall surfaces 413, 414, it is possible to achieve Air flowing in the direction shown is returned more to the downstream side. As a result, it is possible to suppress a distribution in which the flow velocity of air locally increases in the first opening 422 and the fan suction port 210 , and it is possible to suppress noise and flow path resistance.

So far, the embodiment of the present invention has been described with reference to specific examples. However, the present invention is not limited to these specific examples. That is, as long as it has the characteristics of the present invention, structures obtained by adding appropriate design changes to these specific examples by those skilled in the art are also included in the scope of the present invention. Each element included in each specific example described above, and arrangement, material, condition, shape, dimension, etc. of each specific example are not limited to the specific example, and can be appropriately changed.

Claims (5)

1. A vehicle air conditioner, characterized in that it comprises: a centrifugal fan (200) and a housing (400), The centrifugal fan (200) sucks air from the fan suction port (210) in a direction along the rotation axis by rotating around the rotation axis (RC), and blows the air radially, The casing (400) has: a fan housing chamber (440) for accommodating the centrifugal fan; an introduction flow path (420) for allowing the air taken in from the outside flows in a first direction intersecting with the rotation axis and guides the air toward the centrifugal fan; and a wall (421) that connects the fan housing chamber and the introduction flow path separated, and an opening (422) is formed at a position opposite to the fan suction port, and an annular protrusion (431) protruding from the wall to the introduction flow path side and covering the opening is provided on the the periphery of the opening, The vehicle air conditioner is provided with a flange-shaped protrusion (432, 432A), which is arranged at a distance from the wall body, and extends from the ring-shaped protrusion to the opening. The outer side of the part is prominent. 2. The vehicle air conditioner according to claim 1, wherein: The flange-like protrusion is formed over a range from one end (413) to the other end (414) of the introduction flow path in a second direction perpendicular to the rotation axis and the first direction. 3. The vehicle air conditioner according to claim 1, wherein: A protrusion amount of the flange-shaped protrusion from the opening is larger at an upstream side of the flange-shaped protrusion than at a downstream side of the flange-shaped protrusion. 4. The vehicle air conditioner according to claim 1, wherein: A gradual change portion (433) is provided at the end of the annular protrusion on the side of the introduction flow path, The gradient portion has a curved shape with different radii of curvature, The radius of curvature (Ru) of the portion (433u) on the upstream side of the introduction flow path in the transition portion is larger than the radius of curvature (Rd) of the portion (433d) on the downstream side of the introduction flow path in the transition portion. )Big. 5. The vehicle air conditioner according to any one of claims 1 to 4, wherein: The amount of protrusion (Hu) of the portion (431u) on the upstream side of the introduction flow path among the annular protrusions is greater than the protrusion amount (431d) of the portion (431d) of the annular protrusion on the downstream side of the introduction flow path (Hd) large.